EP0080949B1 - Disk brake, and brake shoe for such a brake - Google Patents

Description

The invention relates to a disc brake for a motor vehicle.

The invention relates more particularly to a disc brake of the type comprising a torque support member to which are associated actuation means capable of urging at least one friction element against a rotating disc, said element comprising a lining plate on which is mounted a friction lining, said plate cooperating in anchoring and sliding with guide surfaces formed on the torque support member, at least one anti-noise spring cooperating with said friction element and with said torque support.

A brake of this type which reveals all the characteristics of the preamble of claim 1 or 11 is represented in the French patent published under No. FR-A-2 288 911 and in its first certificate of addition published under No. FR -A-2 311 965. These documents show and describe a disc brake in which the anti-noise spring is locked on the pad holder plate to form with the friction element a subassembly which can be dismantled as a block from the rest of the brake. . For this, the anti-noise spring formed of elastic material has a substantially rectangular portion comprising an opening, two sides of which are placed in the vicinity of the faces of the lining plate, one of the other sides cooperating with the torque support, the other on the other sides cooperating with at least a portion of a bearing portion of a mounting opening formed on the lining plate.

Disc brakes of this type have many advantages compared to conventional disc brakes in which the anti-noise spring is not associated with the friction element, however the mounting of the spring on the lining plate has a certain difficulty in correctly positioning the spring locking system on said lining holder plate. This difficulty leads on the one hand to an increase in the time for mounting the spring on the friction element, and on the other hand has the disadvantage that this installation made by a non-specialist can cause deformation of said spring, this which would cause a loss of force of this spring on the friction element, and the anti-noise function of the spring would be reduced or even canceled.

In order to remedy these drawbacks, the invention provides a disc brake comprising a torque support member with which are associated actuation means capable of urging at least one friction element against a rotating disc said friction element comprising a carrier plate trim on which is mounted a friction lining said plate cooperating in anchoring with guide surfaces formed on said torque support member by means of notches formed on radial edges extending radially from said lining plate at least one anti-noise spring cooperating with said friction element and with said torque support, said lining plate comprising a mounting opening of said anti-noise spring said mounting opening having a support portion said spring cooperates with at least one part of said bearing portion to urge said friction element and is formed by an elastic material having a po substantially rectangular rtion comprising at least one opening, two sides of which are placed in the vicinity of the faces of the packing plate one of the other sides cooperating with said torque support the other of the other sides cooperating with said bearing portion characterized in that said mounting opening has a flared mounting portion limited by first and second lines, said mounting portion opens on the one hand into said bearing portion and on the other hand onto an external peripheral edge of said plate gasket holder and in that said mounting portion opens into said bearing portion at a distance from the adjacent radial edge greater than another distance between the bottom of said notch of the corresponding radial edge and said second line forming said mounting portion and in that the distance between the other two sides of the opening of said spring is less than the distance and greater than said other distance.

According to a particular embodiment of the invention, the disc brake can comprise a single spring cooperating simultaneously with two seal holders and the torque support member.

According to another object, the invention provides a pad comprising a lining plate and a friction lining for disc brake of the type indicated above, said lining plate comprises on an external peripheral edge a mounting opening of an anti-noise spring and notches formed in radial edges extending radially from said lining plate, characterized in that said opening comprising on the one hand a mounting portion flared and limited by first and second lines la widest part of said mounting portion is located at said outer peripheral edge and on the other hand a support portion into which opens the narrower part of said mounting portion and in that said mounting portion opens into said support portion at a distance from the radial edge, and in that this distance is greater than another distance between the bottom of said notch and the second line forming said portion of mounting, to allow the radial introduction of an anti-noise spring into said opening before mounting the pad and to prevent the escape of said spring after mounting the pad.

• - la figure 1 représente une vue de face d'un frein à disque réalisé conformément au principe de la présente invention;
• - la figure 2 est une vue de dessus du frein de la figure 1 ;
• - la figure 3 est une vue en coupe selon la ligne 3-3 de la figure 1;
• - la figure 4 est une vue de face montrant un patin de frein représenté sur les 1 à 3 et 11;
• - la figure 5 est une vue de dessus du ressort anti-bruit représenté sur les figures 1 et 2;
• - la figure 6 est une vue selon la flèche A du ressort de la figure 5;
• - la figure 7 est une vue selon la flèche A du ressort de la figure 5 pour une variante de sa réalisation;
• - la figure 8 est une vue de dessus d'un ressort anti-bruit similaire au ressort de la figure 5 mais réalisé à partir d'une lame élastique;
• - la figure 9 est une vue de face du ressort de la figure 8;
• - la figure 10 est une vue selon la flèche B de la figure 9;
• - la figure 11 est une vue de dessus du frein des figures 1 à 3 équipé d'un ressort anti-bruit selon une troisième réalisation;
• - la figure 12 est une vue de dessus du ressort anti-bruit de la figure 11;
• - la figure 13 est une vue partielle agrandie du frein de la figure 11 montrant le montage du ressort de la figure 12; et
• - la figure 14 est une vue de face du ressort de la figure 12.

An embodiment of the invention will now be described by way of nonlimiting example, adapted to three different embodiments of the anti-noise spring, this with reference to the appended drawings in which:

• - Figure 1 shows a front view of a disc brake produced in accordance with the principle of the present invention;
• - Figure 2 is a top view of the brake of Figure 1;
• - Figure 3 is a sectional view along line 3-3 of Figure 1;
• - Figure 4 is a front view showing a brake shoe shown in 1 to 3 and 11;
• - Figure 5 is a top view of the anti-noise spring shown in Figures 1 and 2;
• - Figure 6 is a view along arrow A of the spring of Figure 5;
• - Figure 7 is a view along arrow A of the spring of Figure 5 for a variant of its embodiment;
• - Figure 8 is a top view of an anti-noise spring similar to the spring of Figure 5 but made from an elastic blade;
• - Figure 9 is a front view of the spring of Figure 8;
• - Figure 10 is a view along arrow B of Figure 9;
• - Figure 11 is a top view of the brake of Figures 1 to 3 equipped with an anti-noise spring according to a third embodiment;
• - Figure 12 is a top view of the noise reduction spring of Figure 11;
• - Figure 13 is an enlarged partial view of the brake of Figure 11 showing the mounting of the spring of Figure 12; and
• - Figure 14 is a front view of the spring of Figure 12.

In Figures 1 to 3, there is shown by way of example a disc brake comprising a caliper 10 slidably mounted by means of two balusters 12 and 14 on a fixed support 16 intended to be associated with a fixed part of the vehicle (not shown). The stirrup 10 overlaps a rotating disc 18 intended to be associated with the vehicle wheel. The caliper 10 has an opening 20 in its part overlapping the disc and acts as a torque support member for two friction elements 22 and 24. The friction element 22 is actuated directly by the piston 26 of a motor brake 28 associated with the caliper 10, while the friction element 24 is associated with the reaction part 29 of the caliper 10 so that it is applied by reaction against the disc during implementation the brake motor 28, the latter forming said actuating means. The friction elements 22 and 24 are received in anchoring and sliding on the circumferentially spaced edges 30 and 32 of the opening 20. The edge 30 comprises an axial key 34 locked by means of a pin 36. This key 34 allows the 'radial extraction of the friction elements 22 and 24 when said key is removed from the brake.

In the embodiment shown, the key 34 and the edge 32 on which the friction elements 22 and 24 are received in anchoring and sliding, are each formed by a surface substantially parallel to the force generated during the coming into contact of the friction linings of the elements 22 and 24 with the disc 18, and a surface inclined with respect to a plane perpendicular to this force at an angle which makes it possible to reduce as much as possible the dimensions of the surfaces constituting the key 34 and edge 32 for a given dimension of the brake, as described in French patent No. 73-39685 published under the number 2 325 298. The key 34 and the edge 32 form the guide surfaces.

As shown more particularly in FIG. 4, each of the friction elements 22 and 24 comprises a lining plate 38 to which a friction lining 40 is fixed, for example by gluing. In addition to the notches 42 and 44 formed on the circumferentially spaced radial edges of the plate 38, the latter has two mounting openings 46 intended to receive an anti-noise spring 48 as shown in FIGS. 1 and 2. In the embodiment shown, the mounting openings 46 are cut from the outer peripheral edge 50 of the lining plate 38. These openings have a first flared mounting portion 52, the widest part of which is located at the peripheral edge 50 and the the narrower part opens into a support portion 54 having the shape of a portion of a circle. It can be seen that the mounting portion 52 is formed by a first broken line 56 having a first portion 56a inclined relative to the peripheral edge 50 and a second portion 56b substantially parallel to the edge 50 and which is tangent to the portion of the circle defining the portion 54. The mounting portion 52 is also formed by a second broken line 58, a first part 58a is substantially perpendicular to the peripheral edge 50, and a second part 58b is inclined and opens out substantially radially in the support portion 54 at a point located at a distance a from the radial edge 60 of the plate 38. It will be noted that the friction elements are substantially symmetrical with respect to the radial plane of symmetry of the brake.

FIG. 5 shows the anti-noise spring 48 of FIGS. 1 and 2. This spring, known per se, is formed by an elastic wire having a substantially rectangular portion 62 whose long sides 64 and 66 are spaced apart by a value slightly greater than the thickness of the lining holder 38. The short sides 68 and 70 are spaced by a value b less than the value a defined previously (see in particular FIG. 4). The side 66 is extended by an arm 72 then bent to form a clamp 74, two variants of which are shown respectively in FIGS. 6 and 7, and which pass on either side of the lining plate 38 shown in dotted lines on the Figures 6 and 7, so as to keep the spring 48 and more particularly the area of the clamp 74 in contact with the outer peripheral edge 50 of the lining plate 38. Referring to Figure 6, we see that the end 76 of the pliers is folded back so that it can be easily mounted on the packing plate, and to be tied thereon to avoid disassembly that is too easy. In Figure 7, the end 76 forms a dulation which makes it possible to hold the clamp 76 simply by rubbing on the packing plate 38.

Figures 8, 9 and 10 show a second embodiment of the anti-noise spring formed in an elastic blade. For this embodiment we will use the same references as those of the first embodiment increased by 100, this for the parts fulfilling the same functions.

Referring to Figure 8, we see that the spring 148 has a rectangular cut 149 near one end of said blade, the two arms of the blade adjacent to the long sides of the cut 149 are separated by a value slightly greater than the thickness of the packing plate. The portions 168 and 170 of the blade located near the short sides of the cutout 149 are spaced by a value c substantially equal to the value b of the first embodiment of the spring, that is to say less than the value a defined above (see in particular Figure 4). The blade is extended by an arm 172 capable of bearing on the external peripheral edge 150 of the lining plate 138. The end of the arm 172 is folded on either side as shown in FIGS. 9 and 10 for forming a clamp 174 in which are formed two tabs 176 obtained by cutting and folding a portion of the clamp 174, these tabs 176 being capable of rubbing on the opposite faces of the lining carrier plate 138 indicated by dotted lines in FIG. 10 .

• L'étrier 10, 110 est préalablement équipé du moteur de frein 28, 128 et des colonnettes 12, 112 et 14, 114. On procède alors au montage du frein sur la partie fixe 16,116 en vissant les vis qui font partie des colonnettes au moyen d'un outil approprié (non représenté) comme représenté sur la figure 3. On équipe alors les éléments de friction 22, 122 et 24, 124 avec des ressorts 48 ou 148 suivant la variante choisie, le montage se faisant de façon similaire pour ces deux variantes. Pour cela on présente le peiti côté 70, 170 dans l'encoche 44 ou 42 de la plaque porte-garniture 38,138. On bascule alors dans le sens de la flèche C de la figure 4 le ressort 48,148 jusqu'à ce que le petit côté 68, 168 pénètre dans l'ouverture de montage 46,146 et plus précisément dans la portion de montage 52,152. On déplace alors le ressort dans le sens de la flèche D de la figure 4 jusqu'à ce que la portion 68, 168 pénètre dans la portion d'appui 54, 154 de l'ouverture 46, 146. On bascule un peu plus le ressort dans le sens de la flèche C de manière à ce que la pince 74, 174 vienne de part et d'autre du bord périphérique 50, 150. Les éléments de friction 22, 122 et 24, 124 sont alors présentés radialement dans le frein en suivant la flèche E de la figure 1. Lorsque les éléments de friction sont dans la position représentée sur cette figure 1, on introduit la clavette 34, 134 dans le sens de la flèche F de la figure 2 pour verrouiller les éléments de friction sur les bords circonférentiellement espacés 30, 130 et 32, 132 de l'ouverture 20, 120 de l'étrier 10,110. On place alors la goupille 36, 136 pour immobiliser la clavette 34, 134. Pour mettre en place les éléments de friction comme indiqué précédemment,le ressort 48,148 a été sollicité dans le sens de la flèche G par la surface de coulissement comme indiqué sur la figure 1. La portion 70,170 étant maitenant en face du bord radial 60,160 de la plaque porte-garniture 38, 138 ne peut s'échapper car la longueur b est inférieure à la longueur a du porte-garniture. Le ressort anti-bruit est donc verrouillé et ne peut s'échapper. La portion 68, 168 du ressort sollicite l'élément de friction selon la flèche H de la figure 1 jouant ainsi le rôle d'antibruit pour l'élément de friction correspondant.

The mounting of the brake which has just been described, and for the two embodiments of the anti-noise spring, is carried out as follows:

• The caliper 10, 110 is previously equipped with the brake motor 28, 128 and the balusters 12, 112 and 14, 114. The brake is then mounted on the fixed part 16,116 by screwing the screws which are part of the balusters by means with an appropriate tool (not shown) as shown in FIG. 3. The friction elements 22, 122 and 24, 124 are then fitted with springs 48 or 148 depending on the variant chosen, the mounting being carried out in a similar manner for these two variants. For this, the small side 70, 170 is presented in the notch 44 or 42 of the lining plate 38, 138. The spring 48,148 is then tilted in the direction of arrow C in FIG. 4 until the short side 68, 168 enters the mounting opening 46,146 and more precisely in the mounting portion 52,152. The spring is then moved in the direction of the arrow D in FIG. 4 until the portion 68, 168 enters the bearing portion 54, 154 of the opening 46, 146. The rocker is tilted a little more. spring in the direction of arrow C so that the clamp 74, 174 comes from either side of the peripheral edge 50, 150. The friction elements 22, 122 and 24, 124 are then presented radially in the brake following arrow E in FIG. 1. When the friction elements are in the position shown in this FIG. 1, the key 34, 134 is introduced in the direction of arrow F in FIG. 2 to lock the friction elements on the circumferentially spaced edges 30, 130 and 32, 132 of the opening 20, 120 of the stirrup 10,110. The pin 36, 136 is then placed to immobilize the key 34, 134. To put the friction elements in place as indicated previously, the spring 48, 148 has been urged in the direction of the arrow G by the sliding surface as indicated on the Figure 1. The portion 70,170 is now facing the radial edge 60,160 of the lining plate 38, 138 cannot escape because the length b is less than the length a of the lining holder. The anti-noise spring is therefore locked and cannot escape. The portion 68, 168 of the spring biases the friction element according to the arrow H in FIG. 1, thus playing the role of anti-noise for the corresponding friction element.

The brake removal operations are carried out in the reverse order to those just described.

Figures 11 to 14 show another embodiment of the brake of Figure 1, and in particular another embodiment of the anti-noise spring. For this embodiment, the same references increased by 200 will be used for parts fulfilling the same functions.

The disc brake of FIG. 11 comprises a caliper 210 mounted to slide on two posts 212 and 214. This brake comprises two friction elements 222 and 224 mounted to slide on the circumferentially spaced edges 230 and 232 of an opening 220 formed in the caliper 210. The caliper 210 comprises a brake motor 228 which acts directly on the friction element 222 to apply the latter to a first face of a rotating disc 218 and to apply by reaction through the reaction part 229 the second friction element 224 on the second face of the disc 218. The peripheral edge 230 of the opening 220 includes a key 234 locked on the caliper 210 by means of a pin 236. The brake is equipped with a spring anti-noise 248 in metal blade cooperating simultaneously with the two friction elements 222 and 224. The friction elements are produced in accordance with the preceding description (see in particular FIG. 4) and include openings d e mounting 246 formed by a mounting portion 252 and a support portion 254.

Referring to Figures 12, 13 and 14 in which is shown the anti-noise spring 248 we see that it has a generally substantially rectangular shape. A first long side 278 cooperates as seen in FIGS. 11 and 13 with the sliding surface of the edge 232. The second of the long sides 280 is supported on each of the friction elements 222 and 224 and more precisely with the broken line 256 forming the mounting portion 252 of the mounting opening 246.

Referring to FIG. 12, it can be seen that the blade has two openings 282 and 284. The opening 282 is of substantially rectangular shape whose long sides 286 and 288 are spaced slightly greater than the thickness of the trim holder plate 238. The pe the sides 290 and 292 are spaced in the circumferential direction of the brake by a value d less than the value defined previously (see in particular FIG. 4). Similarly, the opening 284 has sides 294 and 296 spaced by the same value d. The other two sides 298 and 300 are spaced apart so as to allow the friction element 222 to slide as the friction elements 222 and 224 wear out. As shown in FIG. 13, the sides 290 and 294 respectively of the cutouts 282 and 284 cooperate with the bearing portion 254 of the disassembly opening 246 by means of a folded portion 302 forming a gutter. This folded portion 302 being formed from the metal removed to form the cutouts 282 and 284. As can be seen more particularly in FIG. 13, the folding of the portion 302 has substantially the profile of the support portion 254 and of part of the mounting portion 252.

Referring to Figures 11 to 14 it appears that the folded portion 302 forms with the second long side 280 a gutter with a narrower inlet 304 than the part mounted in the support portion 254. Thus the folded portion forms a guide for a wire for putting on the friction element 222 or 224 an electrical wear indicator (not shown), the wire (not shown) can be passed safely over the disc 218 without risk of damage by the disc 218 or by the wheel rim (not shown) close to the brake. To ensure total security, a wire diameter slightly greater than the inlet 304 will be chosen so that once the wire inside the folded portion cannot escape by itself, or else a given wire diameter, the dimension of the inlet 304 will be adapted so that it opposes the outlet of the wire.

• L'étrier 210 étant préalablement équipé du moteur de frein 228 et des colonnettes 212 et 214, on visse celle-ci dans le support fixe 216 à l'aide d'un outil approprié (non représenté). On met en place les éléments de friction 222 et 224 d'une façon similaire à celle décrite pour le premier mode de réalisation, et on met en place la clavette 234 et l'épingle 236. On présente le ressort 248 dans le sens de la flèche J de la figure 11 de manière à ce que le grand côté 278 du ressort 248 soit en appui sur les éléments de friction 222 et 224, puis en agissant sur le second grand côté 280 dans le sens de la flèche K de la figure 13 on introduit ce grand côté dans la portion de montage 252 puis de nouveau par translation dans le sens de la flèche J on amène ce grand côté et les bords 290 et 294 des ouvertures 282 et 284 dans les portions d'appui 254 des deux éléments de friction. Le grand côté 278 du ressort 248 vient alors sur la surface de coulissement du bord 232 comme indiqué sur la figure 13. Le ressort 248 sollicite alors les plaques porte-garniture 238 selon une direction inverse à celle indiquée par la flèche K appliquée sur la portion d'appui 254, les réactions à cet effort étant appliquées d'une part sur la surface de coulissement au travers du grand côté 278 et d'autre part sur l'élément de friction au travers du deuxième grand côté 280.

The brake which has just been described with the aid of FIGS. 11 to 14 is mounted in the following manner:

• The caliper 210 being previously fitted with the brake motor 228 and the balusters 212 and 214, the latter is screwed into the fixed support 216 using a suitable tool (not shown). The friction elements 222 and 224 are put in place in a similar manner to that described for the first embodiment, and the key 234 and the pin 236 are put in place. The spring 248 is presented in the direction of the arrow J in FIG. 11 so that the long side 278 of the spring 248 bears on the friction elements 222 and 224, then acting on the second large side 280 in the direction of arrow K in FIG. 13 this large side is introduced into the mounting portion 252 then again by translation in the direction of the arrow J, this large side and the edges 290 and 294 of the openings 282 and 284 are brought into the bearing portions 254 of the two elements of friction. The large side 278 of the spring 248 then comes on the sliding surface of the edge 232 as shown in FIG. 13. The spring 248 then urges the lining carrier plates 238 in a direction opposite to that indicated by the arrow K applied on the portion of support 254, the reactions to this force being applied on the one hand to the sliding surface through the long side 278 and on the other hand to the friction element through the second long side 280.

From the above description, it appears that the mounting of the springs is done directly by the mounting openings without requiring specialized labor and without risk of deterioration. In addition, the assembly time is considerably reduced, the springs being ready by their shape for direct mounting, and in the case of the first two embodiments of the spring, the clamp 74, 174 prevents the ends 70 and 170 from being placed in the notches. 42 or 44 before mounting the key 34,134.

The two embodiments which have just been described by way of nonlimiting example, can be easily modified without thereby departing from the scope of the present invention. For example, the shape of the mounting openings can be arranged differently, the broken lines which form the mounting portion can be replaced by non-straight lines, likewise the bearing portion can be of a shape different from the portion of circle as described on the embodiment of the lining plate described. Likewise, the invention can be applied to a disc brake of the fixed caliper type.

Claims (11)

1. A disc brake comprising a torque member (10; 210) having associated therewith actuating means (28; 228) adapted to urge at least one friction member (22, 24; 122, 124; 222, 224) in engagement with a rotating disc (18; 218), said friction member comprising a friction lining support plate (38; 138; 238) and a friction lining (40) mounted thereon, said support plate (38; 138; 238) cooperating in anchoring relationship with guiding surfaces (30, 32; 230, 232) formed on said torque member (10; 210) by means of notches (42; 44) formed on radial edges extending radially (60) of said support plate (38; 138; 238), at least one antirattle spring (48; 148; 248) cooperating with said friction member and with said torque member (10; 210), said support plate (38; 138; 238) comprising a mounting opening (46; 146; 246) of said antirattle spring (48; 148; 248), said mounting opening comprising an engagement portion (54; 154; 254), said spring cooperating with at least one part of said engagement portion (54; 154; 254) for urging said friction member (22; 24; 122, 124; 222, 224) and being formed by a resilient material having a substantially rectangular portion (62; 164-166-168-170; 286-288-290-292-294-296-298-300) including at least one opening (64-66-68-70; 149; 282) having two sides (64, 66; 164, 166; 286, 288) situated adjacent the faces of the support plate (38; 138; 238), one of the other sides (70; 170; 278) cooperating with said torque member (10; 210) and the other of said other sides (68; 168; 290; 294) cooperating with said engagement portion (54; 154; 254), characterized in that said mounting opening (46; 146; 246) comprises a mounting portion (52; 152; 252) enlarged and limites by first (56) and second (58) lines, said mounting portion merges on the one side into said engagement portion (54; 154; 254) and on the other side into an external peripheral edge (50; 150; 250) of said support plate (38; 138; 238), and in that said mounting portion (52; 152; 252) merges into said engagement portion (54; 154; 250) at a distance (a_i) from the adjacent radial edge (60; 160; 260), which is greater than another distance (a₂) between the bottom of said notches (42, 44) of the corresponding radial edge (60; 160; 260), and said second line (58) forming said mounting portion (46; 146; 246), and in that the distance (b, c, d) between the other two sides (68, 70; 168, 170; 290-292, 294-296) of the opening of said spring is smaller than said distance (a₁) and greater than said other distance (a₂).

2. Disc brake according to claim 1, characterized in that, in a manner known per se, said spring (48) is formed by a resilient wire, one (66) of the two sides (64, 66) comprising an extension (72) carrying at its free end a bent portion (74) in engagement with an external peripheral edge (50) of said support plate and axially fixing said extension (72) with respect to said support plate (38), one of the other sides (70) cooperating with said guide surface (32).

3. Disc brake according to claim 2, characterized in that said bent portion (74) forms pincers frictionally cooperating with the faces of said support plate (38).

4. Disc brake according to claim 1, characterized in that said spring (148) is formed by a resilient leaf having a rectangular cut-out (149) forming an opening close to one of the extremities (170) of said leaf, the other extremity (172) of said leaf being in engagement with an external peripheral edge (150) of said friction member (122, 124), one of the other sides (170) cooperating with said guide surface (132).

5. Disc brake according to claim 4, characterized in that at the other extremity (172) of said leaf there are formed pincers (174) frictionally cooperating with the faces of said support plate (138), said pincers (174) being formed by two portions (176) of said other extremity (172), which are radially rebent towards the interior.

6. Disc brake according to claim 1, characterized in that said spring (248) cooperates with two friction members (222, 224) and in that said spring (248) is formed by a resilient leaf of substantially rectangular shape, a first one (278) of the greater sides thereof cooperating with said guide surface (232) and the second (280) of the greater sides being in engagement with each of the support plates (222, 224) said leaf (248) comprising cut-outs (282, 284) having sides (286, 288, 298, 300) that are parallel to the smaller sides of said leaf (248) and disposed on both sides of each of the support plates (238), the other sides (292, 296, 290, 294) thereof being close on the one hand to the first side (278) of the spring (248) and on the other hand to the second greater side (280) of the leaf (248), the other sides (290, 294) of said cut-outs (282, 284) close to the second greater side (280) cooperating with the engagement portions (254) of said support plates (238).

7. Disc brake according to claim 6, characterized in that one (282) of said two cut-outs has an axial width somewhat greater than the thickness of the support plates (238) such as to axially hold stationary said spring leaf (248).

8. Disc brake according to claim 6 or 7, characterized in that said other sides (290, 294) of said cut-outs (282, 284) close to said second greater sides (280) of said leaf (248) are formed by a rebent portion (302) of drop-shape cooperating with said engagement portion (254).

9. Disc brake according to any of claims 6, 7 or 8, characterized in that the length (d) of said cut-outs (282, 284) in a circumferential sense of the brake is smaller than said distance (a,) between an edge (260) extending radially of said support plate (238) and an area where mounting portion (252) merges into said engagement portion (254), and in that said length (d) is greater than said other distance (a₂) between the bottom of said notch (42, 44) and said second line (58).

10. Disc brake according to claim 8, characterized in that said rebent portion (302) of drop-shape forms a guide for an electrical wear-sensing wire adapted to be mounted on a friction member (224) situated on one side of the disc (218) and the information of which is to be transferred to the other side of the disc (218).

11. Brake pad comprising a support plate and a friction lining for a disc brake according to any of claims 1 to 10, said support plate (38; 138; 238) comprising at an external peripheral edge (50; 150; 250) a mounting opening (46; 146; 246) of an antirattle spring (48; 148; 248) and notches (42; 44) formed in said radial edges (60) extending radially of said support plate, characterized in that said opening (46; 146; 246) comprises on the one hand a mounting portion (52; 152; 252) enlarged and limited by first (56) and second (58) lines, with the largest part of said mounting portion being situated at the level of said external peripheral edge (50; 150; 250), and on the other hand an engagement portion (54; 154; 254), into which merges the narrowest part of said mounting portion (52; 152; 252), and in that said mounting portion (52; 152; 252) merges into said engagement portion (54; 154; 254) at a distance (a,) of said radial egde (60), and in that said distance (a,) is greater than another distance (a₂) between the bottom of said notch (42, 44) and the second line (58) forming said mounting portion (52; 152; 252) in order to allow radial introduction of an antirattle spring (48; 148; 248) into said opening prior to assembly of the brake pad, and to prevent dislodgement of said spring after assembly of said brake pad.

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